Torque converter, lock up clutch, master clutch and operator control to provide cushion engagement



Dec. 29, 1964 c. R. HILPERT 3,163,271

' TORQUE CONVERTER, LOCK UP CLUTCH, MASTER CLUTCH AND OPERATOR CONTROL TO PROVIDE CUSHION ENGAGEMENT Original Filed Aug. 3, 1961 3 Sheets-Sheet 1 Dec. 29, 1964 c. R. HlLPl-:RT 3,163,271

TORQUE CONVERTER, LOOK UP CLUTCH, MASTER CLUTCH ANU OPERATOR CONTROL TO PROVIDE CUSHION ENGAGEMENT 3 Sheets-Sheet 2 Original Filed Aug. :5, 1961 Mor y D612 29, 1964 c. R. HILPERT 3,163,271

TORQUE CONVERTER, LOCK UP CLUTCH, MASTER CLUTCH AND OPERATOR CONTROL TO PROVIDE CUSHION ENGAGEMENT Original Filed Aug. 3, 1961 3 Sheets-Sheet 3 Hlm. f mlHHHln. U62

4%/ fffny.

United States Patent O 3 163 271 "roanne convnnran, Locri Un storen, raas- TER CLUTCH AND @PERATR CGNTRQL T PRQVDE CUSHIGN ENGAGEMENT Conrad R. Hilpert, Winnebago, lil., assigner to Twin Disc lutch Company, Racine, Wis., a corporation of Wisconsin @riginal application Aug. 3, 1961, Ser. No. 12%,@38.

Divided and this application heb. 26, 1963, Ser. No.

7 Claims. (Cl. i92-3J2) My invention relates to power transmissions of that type which includes one or more hydraulically actuated fric-tion clutches and a hydraulic torque converter as major components of the power train and more particularly to a control system therefor.

Hydraulically actuated friction clutches have long presented a problem with respect to'securing a smooth, jerkfree engagement of the friction plates. In the usual situ ation and considering an engagement of the clutch, the clutch piston moves for a determined distance from a position of full release to one in which the plates are in contact,V ordinarily termed the hydraulic freeplay. In a typical unit, the clutch piston is moved from release to plate contact position at a relatively low pressure since the only resistance is that due to moving the plates and overcoming the release springs, if any. With the plates in contact, however, axial movement of the clutch piston ceases and the rapid rise in hydraulic pressure causes the clutch plates to take up with a pronounced shock or jerk.

The above objectionable action is believed to be due to the absence of any control on the part of the operator, power transmissions of the type contemplated by this application being usable in wheeled and crawler tractors,

bulldozers, Scrapers, rollers and comparable heavy duty,

reason for lack of response, whether it is due tothe existence of freeplay or to the demand of theload for more torque. It has been applicants experience that the operator will invariably and unwittingly be calling yfor more torque than the situation requires at the instant when the clutch plates are contacted by the piston with instantaneous pressure and torque rises and accompanying jerk.

y Patented ee. 29, lgll ice A further object is to provide a power transmission including a master friction clutch conditioned as above and controlling output of the transmission, a hydraulic torque converter and a hydraulically actuated friction lockup clutch for determining direct drive through the transmission wherein any reduction in pressure applied to the master clutch automatically releases the pressure applied to the lockup clutch.

A further object is to provide a power transmission of the character indicated wherein the `master clutch and hydraulic torque converter are linked in a hydraulic system in such a Way that the basic pressure in the converter is controlled simultaneously with and is dependent upon pressure'applied to the master clutch.

VA further object is theprovision of a control system for the master clutch characterized by a pause position which indicates to the operator that the takeupof the Vhydraulic freeplay is completed at relatively low pressure with the master clutch plates in relatively slipping andlight friction contact and followed by a controlled pressure rise to the maximumengaging pressure.

A further object is to provide -a powervtransmission of the character outlined wherein the master clutch and converter are systemically related so that an oil, constituting the hydraulic element, flows serially through the converter and over the master clutch plates for cooling thereof only when such plates are in contact. i

This application is a division of my copending application, Ser. No. 129,038, filed August 3, 1961.

ln the drawings: v

FIG. 1 is a fragmentary, sectional elevation of one form vof the power transmission, the master and lookup clutches being released.

FIG. 2 is a schematic view of the transmission hy- 'draulic system, partly in section, and including the controis therefor, both clutches being released. Y

FIGS. 3 and 4 are elevations, partly in section, showing positions of a pedal, pause control which are respectively successive to that shown in FIG. 1. v

FIG. 5 is an elevation of a lever mechanism utilizing a detent type of pause control. Y

Referring to FIG. l, there is shown one vform of power transmission embodying certain features ofthe invention, but it will Vbe understood that someaspects thereof, particularly the master clutch and its control, and

, associationwith the hydraulic torque converter, areV ca- Not only does the operator lack knowledge as to the f length of time and control of pressure required for taking up the freeplay, but he is also unable to determine when' possible.

Other considerations'involved in the present invention are the systemic relation in a power transmissionrof a hydraulic torque converter and a pair of hydraulically actuated clutches of the friction type.

One object of the invention is to provide a hydrauli-` cally actuated friction clutch which is Vconditioned so that transition from release to full engagement is atall times under the precise control of the operator.

pable of application to different types of transmission.V

The numeral 1) designates an end ring which is peripherally toothed at 1l for driven engagement with an in` ternally toothed ring'or spider 12 that is connected to a source of power such as an engine. The ring lil is secured to and closes the forward end of a rotating l housing 13 forming part' of a hydraulicV torque converter 14 and the'rear end of the housing 13 encircles and has sealing engagement Vwith a stationary carrier 'V15 and includes a gear 16 for driving a pump that ,services the converter lll andthe master and lookup clutches,all as presentlyfdescribed. From the foregoing,fit will be understood 4that the end ring itl and housingrS rotate' together under the impulse provided by the spider 12 which actually may be the flywheel of the engine.

, reversely curved passage 19 for delivery to radial, inow turbine blades 2t) which are bridged between a core ring 21 and afturbine ring 22 that is keyed to one end of Y a .sleeve shaft 23 whose opposite end connects through a The housing 13 carries radialoutllow impeller blades 17 which are bridged therebetween and a core ring lrand'v the Vworking liquid, assumed toV be a suitable oijl, discharged by the impeller blades flows through. an outer,

master clutch presently described with a gear transmission (not shown)Y ofthe associated vehicle.V Oil dischargedby the turbine blades 2d ows through an inner, reversely curved passage 24 for delivery to radial outflow, stator blades 25 positioned at the inlets of the impeller blades 17 and bridged between a core ring 26 and a stator ring 27 that is fast to the carrier 15.

The impeller, turbine and stator blades 17, 20 and 24, lrespectively, and the passages 19 and 24 are related to form a toroidal working circuit generally designated by the numeral 28. Further, it will berunderstood that the converter 14 is intendedto `be representative generally of suc-l1 a unit and hence neither the shape of the circuit 28 nor the blades sizes and positions are restrictive.

On the converter side of the ring 1i), a ring 29 is secured thereto andis journaled on a bearing 30 carried by the adjacent end of the. sleeve shaft 23 and the latter is journaled in a bearing 31 mounted in the carrier 15. Close to the bearing 30, therinner, peripheral surface of the ring 29 has sealing contact with the shouldered portion 32 ofthe shaft 23to retain the converter oil at this point, while the outer,` peripheral surface ofthe ring 29 has sealing and relative. sliding contact with the inner surface ofank annular piston 33. The outer surface of the piston 33 has like contact with an annular portion 34 of the end ringltl which otherwise denes with the piston 33 and ring 29.A an annular cylinder 35 within vvhich'they piston 33 is slidable and .which communicates through a radial passage 36 recessed in the ring 10`with an annular chamber 37 to the left of the bearing 30. The inner portion of the Vpiston 33 hastoothed, sliding connection with Vthe ring29 .as indicated by the numeral 33 so that the piston 33 always rotateswith the end ring 10 and'hence withgthe converter housing 13.

When pressure is applied Ato the left side of the piston 33 as presently explained, the latter moves to grip an annular, driven, clutch plate 39 againstran inwardly extending, annular portion 4t) of the housing 13 which is positioned between the turbine` ring 22 in the vicinity of the turbine blades 20 and the clutch plate 39.' The inner periphery of the clutch plate 39 has toothed, sliding connection, as indicated by the numeral 41 with an annular oiset 42 provided on the turbine ring 22.

From the above, it will be apparent that, with the clutch plate 39 in the release positionrshown `in FIG. l, and the enginerriurnningrthe drive is through the `converter 14 with theusual torque multiplication. For direct drive, the piston 33 is pressure moved to engage the clutch plate 39 against the housing portion 4i) to` thereby cause the turbine ring 22 to rotate at the same speed as the housing 13. The piston 33, plate 39 and housing portion 40'together constitute alockup clutch 43. y Y Y Y Y Workingoil at a predetermined pressureris supplied to the converter 14, whenever oil pressure is present in the engaging chamberof thepmaster clutch as presently de-r scribed, througha passage-Min the carrier 15and Vows outward between thestator ring 27` andthe adjacent end of the housing 13 for delivery to the toroidal circuitY 28 between the outlets of the stator blades 25 and the inlets of theimpellerblades 17. VWhen present in the converter 14, the oil completely lls the toroidal circuit 28 and also they annular chamber 45 between therturbine ring 22 and the ring 29, piston 33 and housingiportionrdgil. The pres sureof theconverter oil biases the lockup clutch piston 33 to the release position shown;

between the interior of the sleeve shaft 23 and a power takeoff shaft 54 which extends therethrough, the delivery end of the passage 53 communicating With the annular chamber 37 and hence with the lookup clutch cylinder 35. The left end of the power takeoff shaft 54 has splined connection with a hub 5S forming part of the end ring 10 and so always rotates at engine speed while the opposite end Vof the shaft V5,4 has bearing support in the output end of the sleeve shaft 23 and extends therebeyond for conventional attachment to a variety of implements.

The right or output end of the sleeve shaft 23 has splined connection with a hub 56 suitably held against axial movement and having integrally formed therewith a back plate 57 serving as an abutment against which a plurality of clutch plates, generally indicated by the numeral 58, are gripped. Alternate plates have driven and relative sliding engagement with the hub 56 while the intervening clutch plates have driving and relative sliding engagement with a toothed annulus 59 forming part of a spider 60 whose hub 61 has a conventional connection with a gear transmission (not shown) with the driving axle of thervehicle.

Carried by and rotating `with the sleeve shaft 23 and held van annular rib 62 on the shaft 23 is an annular reaction plate 63 in sealed relation thereto is a cylindrical shell 64. Preferably integral with the shell 64 at one end thereof is an annular piston 65 for engaging the clutch plates 58 and which is sealably slidable on a sleeve 66 forming part of the reaction plate 63v and defines therewith, the sleeve 66 and shell 64 an annular engaging chamber 67 to which oil under controlled pressure is supplied as desired and as subsequently described. Y

The opposite end of the shell 64` carries internally thereof and fasttthereto a ring 68 whose inner peripheral surface is slightly spaced froman annular shoulderr69 providedon a ring 70 which tits within a recessed part 71 ofV and forms a part of the carrier' 1,5. The ring 68 defines with the shell 64, reaction plate 63 and sleeve 69 an annular balance chamber 'i` vand the Vspacing of the ring 68 from the sleeve y69 deiines an annular throttling passage 73 Vproviding communication between the balance chamber 72 and a sump for a purpose presently explained. A release spring, specifically shown asa Belleville spring 74, is positioned in the, balance chamber 72 and biases the assembly including the shell 64, piston 65 and ring For the engaging chamber 67, relatively high pressure oil', controllable by the operator, is delivered by a pipeV 75 for flow through connecting passages 76A and 77 in the carrier 1S and ringr70, respectively. The delivery endof the passage 77V connects through an annular chanf Oil is discharged from theY toroidal circuit 28 through an annular opening'46 communicatingrpwith the passage 24 and located between the turbine and stator Vrings 22 and 27, respectively, and into an annularV chamber 47V`in'- ,f

eluded between the carrierlS and the last vnoted rings. From the chamber 47, the oililows into a passage'48 provided inthe carrier 15 and from t-hence tocertain parts kot the master jclutch assemblyin a manner and for pur- 52`inrthe sleeve'shaft 23 to an annular passage 53 included nel 78 and radial passage 79 in the sleeveshapft 23 `with one end of a longitudinalchannel 80 providedin the outer surface of va :sleeve 81 which iscoaxial Ywith and positioned in a counterbored portion` 82 .of the sleeve shaft 23, the sleeve 81 rotating with the sleeve shaft 23 and beingspaced from the power Vtakeoff shaft 5,4;` The opposite end of the channel'80 connects successively througha radial passage 83 and an annular 'channel' 84 in the sleeve shaft 23 and aY passage 85 in the (reaction plate 63 with the engaging l chamber 67 r For the balance chamber 72, the oil discharging yfrom the hydraulic torque converter 14 to the passage 4821s described above flows successively :through a passage 86 83 including a throttling oriiice 89 inthe ring 70Yto thew balancek chamber 72'and the remainder moving'succesul u sively through a radial passage 99 in the sleeve shaft 23, a longitudinal channel in the sleeve S1 and a radial passage 92 in the sleeve shaft 23 into a plurality of pockets 93 spaced around the hub 56 from which thev oil centrifugally ows over the clutch plates 58 for cooling.

The foregoing structure is incorporated in a hydraulic system as schematically shown in FIG. 2 to which reference will now be made.

The system oil is Withdrawn from a convenient sump 94 by a pump 95 driven by the gear 16 (see FIG. l) and passed through a heat exchanger 96 to an inlet port 97 intermediately positioned in a control valve 9S. Slidable in the valve 9S is a spool type, valve stem including an intermediate land 99 which connects by reduced necks 19t) and 101 with end lands 192 and 193, all respectively. The valve 98 also includes an outlet port 134 connecting with the sump 94 and an outlet port 165 connecting with operator controlled, pressure regulating valve presently described. In the position of the valve 9S shown in FiG. 2, the intermediate land 99 directs all output of the pump 95 to the sump 94 and pressure therefore does not exist in the port 105 and this valve position determines full release positions of the direct drive clutch 43 and also of the clutch which includes the plates 55, now designated as the master clutch 105.

The control valve 98 is conditioned to establish pressure in the port 195 and to deny ilow to the sump 94 through the port 194 by shifting the valve stem until the intermediate land 99 is to the left `of the inlet port 97 and at this time, the land 192 abuts a stop 107. accomplish this movement, an arm 1t8lextends longitudinally from the land 163 and terminates in a transversely disposed ear 169 which is positioned in generally opposed relation to the adjacent end of the land 193. The arm 108 also carries a lug 110 which is spaced from the ear 169 in the direction of the land 1113 and extends from the same side of the arm 108 as does the ear 169. A helical spring 111 is interposed between the end Vof the land 193 and a plate 112 which, when the control valve 98 is in the position shown in FlG. 2, abuts the lug 11).

The port 105 communicates with a chamber 113 in which is reciprocable a pressure regulatingV valve 114 and the chamber 113 further includesV outlet ports 115 and 116 in which the pressure is determined by the position of the regulating valve 114. The opposite'ends of a helical spring 117 respectively abut the'regulating valve 114 and a push plate 11S which is movable in the manner presently described to load the spring 117 and thus determine pressures in the outlet ports 115 and 116.

The outlet port 115 communicates with the intake of the hydraulic torque converter 14 by what is shown entirely as a pipe 119 in FIG. 2, but it will be understood that the pipe 119 functionally includes the passage 44 in FIG. l. The other outlet port 116 connects in FEiG. 2 by the pipe 129 with the engaging chamber 67, the pipe 120 representing collectively the pipe 75 and the ensuing passages and channels above referred to and leading to the chamber 67 and as shown in FlG. 1, the pipe 12()` being the relatively high pressure line.

Tapping the pipe 1211 is a pipe 121 whose outlet connects with a chamber 122 in which is exposed one end or" a piston 123 whose opposite end is enlarged to provide a pressure regulating valve 124 that is exposed in a chamber 125. The opposite ends of a ypipev 126 connect respectively with the outlet of the converter 14 and the 6 14 With the balance chamber 72, the pipe 128 representing collectively in FlG. l the passages 48, 86, chamber 87 and passage 83.

For the direct drive clutch 43, a control valve 129 of the spool type determines the application of high pressure oil thereto and includes lands 139 and 131 connected by a reduced neck 132. In the position shown in FIG.`2, the land 131 masks the outlet end of a pipe 133 which connects with the high pressure pipe and the direct drive clutch cylinder 35 connects through a pipe 134 with a chamber 135 between the lands 13%) and 131 and thence with the sump 94 so that the direct drive clutch 43 stands released. The pipe 134 in FIG. 2 represents collectively the pipe 49 and the ensuing passages and channels leading to the direct drive cylinder 35 as shown in FIG. 1.

An important feature of the invention resides in the knowledgeable control on the part of the operator ofthe apply pressure between full release and full engagement of the master clutch 106 and of the torque outputof the transmission up to the respective maximum values thereof. One medium of control, in conjunction With the pertinent parts described above, takes the form of a'pedal V136 whichV is pivoted at one end on a base 137 that may be provided by the associated vehicle `or by a convenient part of the transmission and interposed between the opposite or free end of the pedalg136 and the base 137 is a helical spring 13S. Also acting against the pedal 136 between the pivot thereof and the spring 13e and during a stated portion of pedal movement, which is upward from the position sho-wn in FIG. 2, is the closed end 139 of a housing 140 which is slidable through the base 137 and encloses a helical spring 141 which is interposed between the housing end 139 and a part 142 of the base 137. In the PIG. 2 position, the spring 141 is fully loaded and upward movement of the housing 1411 under the thrust of the spring 141 and as permitted by upward movement of the pedal 136 is limited by housing ears 143 which engage the under side of the base 137. p-

Fixedly connected to the opposite end of and moving with the pedal 13d is one end of an arm 144 whose opposite end connects in such a way with one end of a pushrod 14S that swings of the arm 144 ett-ect longitudinal movements of the pushrod 145. The opposite end of the pushrod 145 carries laterally disposed and oppositely eX- tending arms 147 and 148. The arm 147 terminates in a T 149 which is positioned between the ear 199 and plate 112 so that when the pushrod 145 is moved in opposite directions, respectively, the T 149-either engages the plate l 112 and loads the spring 111 or engages the ear 1tl9with resultant position changes in the control valve 98. The other pushrod arm 143 is, in the position of parts shown' systemic control, it will be assumed that the engine is idling andV that the several parts occupy the positions shownVV in FIG. 2. Since the pedal 136 is then depressed `by the operator to its lowermost position as in FIG. 2 to thereby load the springs 13d and 141, the control valve 98 directs j the entire output of the pump 95Vtothesu'mp 94 and pressure does not exist in the outlet ports 115 and 116y of theY pressure regulating valve 114. The master clutch 106 and the direct drive clutch 43 therefore are released and there is no oil iiowto the converter l14 and to the plates;V of the master clutch 166. The foregoing represents the systemic condition when a shift is made in the associated gear transmission and if the latter is of the clash gear type,V gear meshing is facilitated due to the absence of oil flow over the plates of the master clutch ltirwhchmaterially i reduces the vdrag of such plates.

7 vehicle is setin movement by drive through the converter 14 and, for this purpose, the operator permits the pedal 136 to swing upwardly due-to the thrust of the springs 138 and 141-, but under the control of the operator so that the pushrodl 145 begins moving towards the left and the T '149 begins to compress the spring 111 and to eitect a leftward shift of the control valve 98 until its land 102 abuts the stopw1`07. All output of the pumpv 95 is then directed to the outlet port 105 and thence to the chamber 113. Oil then begins flowing through the pipe 13129,converter14kpipe 126, chamber 125, land pas-sage 127 to the plates of the master clutch 166 and thence to the sump 94, also through the pipe 12) to the engaging chamber 67 and through the pipe 121 to the chamber 122, and through the pipe 12,8 tothe balance chamber 72.` The purposeV of the latter chamber is to centrifugally balance its oil contentwith that in thek engaging chamber 67. Whenpressureexists in the pipe 128, the oil in the balance chamber 72-ows to the 'sump 94 through the throt'tling passage 73.

`After the land 102 abuts the stop 1117, continued movement of the pushrod 145 contacts its arm 143 withthe push plate 118 to therebyetlect through the spring 117 movementof the pressure regulating valve 114 towards the left. This movement of the valve 114 begins to par'- tially close the port 115 so that the pressure in the port 116 begins to rise relative to that in the port 115 'and starts the piston 65 moving in a master clutch` engaging direction. The same pressure rise is activeY against the exposed end of theA piston 123 which shifts the pressure regulating valve 124 to theright to raise the pressure in the chamber 125 and so establish a basic Working pressure in the converter 14, assumed by way of example to be 40 p.s.i. This basic converter Ypressure is reached when the maximum pressure is applied to the engaging chamber 67 as will be subsequently described. y

The upward movement of the pedal 136 with accompanyin-g shiftv of the pushrod 145 continuesV under the restraint imposed by the operator, foot or hand, until the housing ears 143 engage the base 137 (see FiG. 3). The movement of the piston 65 from the full release posivtion shown in FIG. 2 to that in which the plates of the master clutch 166 are placed in incipient contact is accomplished at relatively low pressure since the pressure regulating vvalve 114 has not yet reached a position establishing maximum engaging pressure for the master clutch,

assumed by Way of example to ybe 150 p.s.i.

The stoppage of the housing 140-by the ears 143 provides a limit for exerting pressure by the housing 140' against the pedal 13o and this position is immediately felt by the operator due to the reduction in spring pressure acting against the pedal 136. At this point, LVtermed'tlie pause position, the operator holds the pedal 134.5V stationary and Waits until the plates of the master clutch 166 are in relative sliding contact at the indicated relatively low pressure. Knowledge of this conditioning of the plates 58 of the master clutchl 166, is immediately known to the operator from'the overall characteristics of the situation'. For example, the engine is now under slight load which will occasion a change in its'tone and there may be a typical' soundA emitted Vby the drive lines coming` under torque. Importantly at this stage of the situation,

the pressure in the engaging chambero'l is not'only'relatively low, but vit is aV pressure which hasbeen consciously ,A establishedv byfoperator control.

Thereafter, the pedal 136 continuesits upward move- ,rnent due to the thrust of` the spring 13S and under opera- K tor restraint to the other terminal position shown in FIG. 4. During this movement, the pushrod'arm 148con`tinues to load the vspring 117 through-the push plate 118. with consequent further pressure Vrise inthe'e'n'gaging charnber 67 up to the 'maximum value yand at this point, the

arms 147V and v14S'occupy generally therdotted positions shown in FIG. 2. This pressurerise is gradual and is reflected in a gradually increasingV output torque and both control of` the operator.

irst contact or thereafter. Moreover', this type of control is particularly useful in inching movements of the vehicle for obvious reasons. The springs shown in FIG; 2 are related to insure the foregoing operation;

From the above, it will be apparent that the pause position provides a deinite point in the control at'which to wait for the indication of clutch plate contact atv the relatively low pressure, the operator determining when and the time of application. operator determines the initiation ofrthis rise from the relatively low value and the gradual increase in the rise up to maximum engaging value.

The arrangement of the pedal 136' and its thrusting springs 13S and 141 is intended to generally show a mech` anism which is sensing with respect to the feel of the operator by reason of the sharp change in spring rate. Other sensing variations may be employed such as aclick provided by a detent structure. A

,Considering direct drive, it will be apparent that with the parts positioned as shown in FIG. 2, the direct drive clutch 4?:V cannot be engaged merely by shifting the control valve 129 to the left to connect the pipes 133 and 134.

At this time, pressure is non-existentin the chamber 113,' and the pedal is operator held down in the position` shown in FIG. 2 so that the arm 14S blocks movement of With maximum pressure established in the chamber 113y and the arm 14S therefore occupying the dotted position shown in FIG. 2, it is possible for the operator to shift the control Valve 129 to the left and thus connect the pipes 133 and 134 to apply the relatively high pressure to the direct drive clutch 43. This conditioning does not affect the application of the same pressure to the master clutch 106. The porting of the control valve 129 is such that the direct drive clutch 43 cannot be engaged until the regulating valve 114 has established the relatively high pressure in the chamber 113. In lthe event that pressure in the chamber V1155 is reduced by control on the regulat- Y ing valve-'114, the engagement of the arm 143 With the arms 150 immediately returns thecontrol Valve 1129 to the position shown` in FIG. 2 and fthus connects the direct drive clutch cylinder 35 with the sump 94. This safety arrangement'prevents slipping of the direct drive clutch 43;

It will be apparent further that With the parts conditioned as in FG. 2, oil is not supplied to the converter 14 and the plates of the master clutch 106, but when thel transmission is conditioned for service, cooling oil flows serially through the converter and over the indicated plates. Moreover, the converter basic pressure is controlled simultaneously with andis dependent upon the clutch pressure. Y Y

ln FlG. V5 Vis shown a variant control linkage which may be used in place of the pedal assembly shown in FIG. 2. Hand lever 151 is intermediately pivoted at 152 on a convenient part of the transmission or Vehicle designated by the numeral 153 and the end of the lever 151 'Y opposite its handgripis` pivotally connected to one end of Va link 154 Whose Vopposite end pivotally connects'with lation of the pushrod 145. The levericarries an offset 155' which includesl a curved track 156 kprovided with a transverse groove 157 at a designated point thereof. The free, parti-arcuateend 15S of. a U-shaped spring 159is condi-` tioned to ride along the track;156 and the opposite end of the-spring 159 is fast to aconvenient base 160.- Y

During pressure rise, the` When the parts are in the full line positions shown in FIG. 5, the transmission is conditioned as in FIG. 2, both clutches being released and the lever 151 and its associated parts functionally corresponding to the pedal 136 and its immediately associated parts.

To start the operation, the lever 151 is moved clock- Wise with the spring end 158 riding along the track 156 until it engages the groove 157. This engagement can be felt by the operator and the lever is then in the pause position as dened and described above. After the termination of the pause period, the operator further moves the level 151 clockwise with effects on the transmission as already outlined until it reaches the dotted position shown which determines the maximum .torque transmit-k ting condition of the master clutch 1%. In the latter position of the lever 151, the pivotal connection 161 of the link 154 therewith is in overcenter and locked relation with respect to the pivot 152 of the lever 151 and the pivot connection 162 of the link 154 with the pushrod 145. The clockwise movement of the lever 151 is made against the pull of a spring 163 whose opposite ends are respectively connected to the adjacent end of the pushrod 145 and a convenient part 164. When the lever 151 is moved towards the full line or clutch disengaged position, it is only necessary to break the overcenter condi-tion and then the spring 163 tal-.es control and returns the pus'nrod 145 to the release position shown in FlG. 2.

I claim:

1. A power transmission comprising a hydraulic torque converter an oil actuated friction plate clutch providing a connection between a load and the converter output, a pressure liquid source, a. irst pressure regulating valve communicating With the source, rst and second oil circuit means providing outlets of the first pressure regulating valve, the tirst circuit means including the converter and disch-arging over the clutch plates for cooling thereof and the second circuit means supplying engaging pressure to the clutch, a second pressure regulating valve having one end subjected to pressure from the second circuit means and its opposite end exposed to oil flow in the iirst circuit means on the discharge side of the converter, and operator controlled means for varying the position of the iirst pressure regulating valve to determine the application of selected pressures to the clutch including the maximum engaging pressure, the second pressure regulating valve being arranged to establish in the converter a basic pressure lower than and when the maximum pressure is applied to the clutch.

2. A power transmission as dened in claim 1 wherein a control valve is interposed between the pressure liquid source and the inlet of the irst pressure regulatingvalve for determining the admission of pressure liquid thereto, and the operator controlled means is common to-the control and rst pressure regulating valves and is movable to first advance the control valve to a stop position admitting pressure liquid to the iirst pressure regulating l@ Y valve and to thereafter variably position the last named valve.

3. A power transmission' as dened in claim l wherein the clutch includes a piston member and a chamber for receiving pressure liquid to move the piston member towards the plates, and the operator controlled means varies the position of the iirst pressure regulating valve between limit positions thereof respectively determining full release of the plates and a relatively high pressure in the chamber to establish a maximum torque transmitting condition of the plates and including an intermediate position, and means associated with the operator controlled means and operable at said intermediate position corresponding to a first pressure regulating valve position determining a relatively low pressure in the chamber to provide a sensing signal to the voperator to pause in said intermediate position until the plates are in relative sliding contact, continuing movement of the operator vcontrolled means thereafter establishing varying tirst pressure regulating valve positions determining a gradual pressure rise in the chamber to maximum value.

4. A power transmission as delined in claim 3 wherein the operator vcontrolled means includes a rockable pedal and the means associated with the operator controlled means comprises a plurality of spring means compressed by the pedal when in a position determining full release of the plates, and means for preventing thrusting of some of the spring vmeans against the pedal when the latter reaches said intermediate position to provide an operator sensing signal.

5. A power transmission as defined in claim 1 wherein the converter includes a rotating housing having an impeller and a turbine connected to the input of the oil actuated friction plate clutch a direct drive, oil actuated clutch is mounted in the housing and engageable to lock the housing and turbine for rotation together, and a control valve is movable between positions determining release and a tapping of the second oil circuit means to provide engagement of the direct drive clutch.

6. A power transmission as defined in claim 5 wherein the operator controlled means includes a part barring movement ot' the control valve to a position engaging the direct drive clutch until the maximum engaging pressure is applied to the lirst named clutch.

7. A power transmission as detined in claim 6 wherein said part returns the control Valve to a position releasing Y References Cited in the le of this patent UNITED STATES PATENTS 2,833,385 Peterson et a1.' 'May 6,1958

Black et al avan-f Jail, 24, 1961 

1. A POWER TRANSMISSION COMPRISING A HYDRAULIC TORQUE CONVERTER AN OIL ACTUATED FRICTION PLATE CLUTCH PROVIDING A CONNECTION BETWEEN A LOAD AND THE CONVERTER OUTPUT, A PRESSURE LIQUID SOURCE, A FIRST PRESSURE REGULATING VALVE COMMUNICATING WITH THE SOURCE, FIRST AND SECOND OIL CIRCUIT MEANS PROVIDING OUTLETS OF THE FIRST PRESSURE REGULATING VALVE, THE FIRST CIRCUIT MEANS INCLUDING THE CONVERTER AND DISCHARGING OVER THE CLUTCH PLATES FOR COOLING THEREOF AND THE SECOND CIRCUIT MEANS SUPPLYING ENGAGING PRESSURE TO THE CLUTCH, A SECOND PRESSURE REGULATING VALVE HAVING ONE END SUBJECTED TO PRESSURE FROM THE SECOND CIRCUIT MEANS AND ITS OPPOSITE END EXPOSED TO OIL FLOW IN THE FIRST CIRCUIT MEANS ON THE DISCHARGE SIDE OF THE CONVERTER, AND OPERATOR CONTROLLED MEANS FOR VARYING THE POSITION OF THE FIRST PRESSURE REGULATING VALVE TO DETERMINE THE APPLICATION OF SELECTED PRESSURES TO THE CLUTCH INCLUDING THE MAXIMUM ENGAGING PRESSURE, THE SECOND PRESSURE REGULATING VALVE BEING ARRANGE TO ESTABLISH IN THE CONVERTER A BASIC PRESSURE LOWER THAN AND WHEN THE MAXIMUM PRESSURE IS APPLIED TO THE CLUTCH. 